JP2022051623A - Refrigeration cycle device - Google Patents

Abstract

To perform defrosting as efficient as possible in a refrigeration cycle device absorbing heat from ambient air.SOLUTION: A refrigeration cycle device comprises: a heat radiation part 12 which radiates heat of coolant discharged from a compressor 11; a decompression part 16 which reduces pressure of the coolant radiated at the heat radiation part; an evaporation part 17 which cools a heat medium by thermally exchanging the heat medium with the coolant depressed at the decompression part; an ambient air endothermic part 45 which causes the heat medium cooled at the evaporation part to absorb heat from the ambient air; heat sources 25, 82 which heat the heat medium by radiating heat to the heat medium; first circulation circuits 20, 80 which circulate the heat medium to the heat sources; a second circulation circuit 30 which circulates the heat medium between the evaporation part and the ambient air endothermic part; and flow channel changeover parts 26, 60, 83 which determine whether or not defrost of the ambient air endothermic part is necessary and circulate the heat medium by the first circulation circuits and the second circulation circuit individually when it is determined that the defrost of the ambient air endothermic part is unnecessary, and meanwhile, switch a flow channel of the heat medium so as to circulate the heat medium of the first circulation circuits to the ambient air endothermic part when it is determined that the defrost of the ambient air endothermic part is necessary.SELECTED DRAWING: Figure 5

Description

The present invention relates to a refrigeration cycle device that absorbs heat from the outside air.

Conventionally, Patent Document 1 describes a heat pump system including an LT radiator as an outside air endothermic device. In the LT radiator, the cooling water cooled by the refrigerant in the chiller absorbs heat from the outside air. The cooling water temperature when cooled in the chiller may be 0 ° C or lower, and when the cooling water temperature is 0 ° C or lower, the water in the outside air solidifies on the surface of the LT radiator and frost adheres ( So-called frost).

In this conventional technique, cooling water heated by a water-cooled condenser is supplied to the LT radiator, and frost adhering to the surface of the LT radiator is melted and removed (so-called defrosting).

Japanese Patent No. 6399060

In the above-mentioned prior art, there is no mention of when and how to defrost the most efficient heat pump system (in other words, a refrigeration cycle device that absorbs heat from the outside air).

In view of the above points, it is an object of the present invention to perform defrosting as efficiently as possible in a refrigeration cycle apparatus that absorbs heat from the outside air.

In order to achieve the above object, the refrigeration cycle apparatus according to claim 1 is used.
A compressor (11) that sucks in the refrigerant, compresses it, and discharges it.
A heat radiating unit (12) that dissipates heat from the refrigerant discharged from the compressor,
A decompression unit (16) that decompresses the refrigerant radiated by the heat radiating unit, and
An evaporating unit (17) that evaporates the refrigerant and cools the heat medium by exchanging heat between the decompressed refrigerant and the heat medium in the decompression unit.
The outside air endothermic part (45) that absorbs heat from the outside air to the heat medium cooled by the evaporation part,
Heat sources (25, 82) that radiate heat to the heat medium and heat the heat medium,
The first circulation circuit (20, 80) that circulates the heat medium to the heat source,
The second circulation circuit (30) that circulates the heat medium between the evaporation part and the outside air heat absorption part,
Determine if defrosting of the outside air heat absorption part is necessary,
When it is determined that defrosting of the outside air heat absorbing part is not necessary, the heat medium is circulated separately in the first circulation circuit and the second circulation circuit.
When it is determined that defrosting of the outside air heat absorbing part is necessary, the flow path switching unit (26, 60, 83) that switches the flow path of the heat medium so as to circulate the heat medium of the first circulation circuit to the outside air heat absorbing part. To prepare for.

According to this, defrosting can be reliably performed when defrosting of the outside air heat absorbing portion is required, so that defrosting can be efficiently performed.

The reference numerals in parentheses of each means described in this column and the scope of claims indicate the correspondence with the specific means described in the embodiments described later.

It is an overall block diagram of the refrigeration cycle apparatus in 1st Embodiment. It is a block diagram which shows the electric control part of the refrigeration cycle apparatus in 1st Embodiment. It is an overall block diagram which shows the operating state in the waste heat defrosting mode of the refrigerating cycle apparatus in 1st Embodiment. It is an overall block diagram which shows the operating state in the heating heat defrosting mode of the refrigerating cycle apparatus in 1st Embodiment. It is a flowchart which shows the control process of the control program in 1st Embodiment. It is a determination diagram used for the frost formation determination of a common radiator in the control process of the control program in 1st Embodiment. It is a time chart which shows one operation example of the refrigeration cycle apparatus in 1st Embodiment. It is a time chart which shows the other operation example of the refrigeration cycle apparatus in 1st Embodiment. It is an overall block diagram of the refrigeration cycle apparatus in 2nd Embodiment. It is an overall block diagram which shows the operating state in the heating heat defrosting mode of the refrigerating cycle apparatus in 2nd Embodiment. It is a flowchart which shows the control process of the control program in 3rd Embodiment. It is a time chart which shows one operation example of the refrigeration cycle apparatus in 3rd Embodiment.

Hereinafter, embodiments will be described with reference to the drawings. In each of the following embodiments, the parts that are the same or equal to each other are designated by the same reference numerals in the drawings.

(First Embodiment)
Hereinafter, embodiments will be described with reference to the drawings. The vehicle air conditioner 1 shown in FIG. 1 is an air conditioner that adjusts a vehicle interior space (in other words, an air conditioning target space) to an appropriate temperature. The vehicle air conditioner 1 has a refrigeration cycle device 10.

The refrigeration cycle device 10 is mounted on an electric vehicle, a hybrid vehicle, or the like. An electric vehicle is a vehicle that obtains a driving force for driving a vehicle from a traveling electric motor. A hybrid vehicle is a vehicle that obtains driving force for driving a vehicle from an engine (in other words, an internal combustion engine) and an electric motor for traveling.

The refrigerating cycle device 10 is a steam compression type refrigerator including a compressor 11, a condenser 12, a first expansion valve 13, an air side evaporator 14, a constant pressure valve 15, a second expansion valve 16, and a cooling water side evaporator 17. be. The refrigeration cycle apparatus 10 of the present embodiment uses a fluorocarbon-based refrigerant as the refrigerant, and constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure side refrigerant does not exceed the critical pressure of the refrigerant.

The second expansion valve 16 and the cooling water side evaporator 17 are arranged in parallel with the first expansion valve 13, the air side evaporator 14, and the constant pressure valve 15 in the refrigerant flow.

A first refrigerant circulation circuit and a second refrigerant circulation circuit are formed in the refrigeration cycle device 10. In the first refrigerant circulation circuit, the refrigerant circulates in the order of the compressor 11, the condenser 12, the first expansion valve 13, the air side evaporator 14, the constant pressure valve 15, and the compressor 11. In the second refrigerant circulation circuit, the refrigerant circulates in the order of the compressor 11, the condenser 12, the second expansion valve 16, and the cooling water side evaporator 17.

The compressor 11 is an electric compressor driven by electric power supplied from a battery, and sucks in the refrigerant of the refrigerating cycle device 10, compresses it, and discharges it. The electric motor of the compressor 11 is controlled by the control device 60 shown in FIG. The compressor 11 may be a variable displacement compressor driven by a belt.

The condenser 12 is a high-pressure side heat exchanger that exchanges heat between the high-pressure side refrigerant discharged from the compressor 11 and the cooling water of the high-temperature cooling water circuit 20. The condenser 12 is a heat radiating unit that heats the cooling water by exchanging heat between the refrigerant discharged from the compressor 11 and the cooling water to dissipate the refrigerant.

In the case of an electric vehicle, the compressor 11 and the condenser 12 are arranged in the motor room of the vehicle. The motor room is a space in which a traveling electric motor is housed. In the case of a hybrid vehicle, the compressor 11 and the condenser 12 are arranged in the engine room of the vehicle. The engine room is the space where the engine is housed.

The condenser 12 has a condensing unit 12a, a receiver 12b, and a supercooling unit 12c. In the condenser 12, the refrigerant flows in the order of the condensing section 12a, the receiver 12b, and the supercooling section 12c.

The condensing unit 12a condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant discharged from the compressor 11 and the cooling water of the high-temperature cooling water circuit 20.

The receiver 12b is a gas-liquid separation unit that separates the gas-liquid of the high-pressure refrigerant flowing out from the condenser 12, causes the separated liquid-phase refrigerant to flow out to the downstream side, and stores the excess refrigerant in the cycle.

The supercooling unit 12c supercools the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant flowing out from the receiver 12b and the cooling water of the high temperature cooling water circuit 20.

The cooling water of the high temperature cooling water circuit 20 is a fluid as a heat medium. The cooling water of the high temperature cooling water circuit 20 is a high temperature heat medium. In this embodiment, as the cooling water of the high temperature cooling water circuit 20, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid is used. The high temperature cooling water circuit 20 is a first circulation circuit in which cooling water circulates. The high-temperature cooling water circuit 20 is a high-temperature heat medium circuit in which a high-temperature heat medium circulates.

The first expansion valve 13 is a first decompression unit that decompresses and expands the liquid phase refrigerant flowing out of the receiver 12b. The first expansion valve 13 is an electric expansion valve. The electric expansion valve is an electric variable throttle mechanism having a valve body configured to change the throttle opening degree and an electric actuator for changing the throttle opening degree.

The first expansion valve 13 is a refrigerant flow switching unit that switches between a state in which the refrigerant flows in the air-side evaporator 14 and a state in which the refrigerant does not flow. The operation of the first expansion valve 13 is controlled by a control signal output from the control device 60.

The first expansion valve 13 may be a mechanical temperature expansion valve. When the first expansion valve 13 is a mechanical temperature expansion valve, an on-off valve that opens and closes the refrigerant flow path on the first expansion valve 13 side needs to be provided separately from the first expansion valve 13.

The air-side evaporator 14 is an evaporator that evaporates the refrigerant by exchanging heat between the refrigerant flowing out from the first expansion valve 13 and the air blown into the vehicle interior. In the air side evaporator 14, the refrigerant absorbs heat from the air blown into the vehicle interior. The air-side evaporator 14 is an air cooler that cools the air blown into the vehicle interior.

The constant pressure valve 15 is a pressure adjusting unit that maintains the pressure of the refrigerant on the outlet side of the air side evaporator 14 at a predetermined value. The constant pressure valve 15 is composed of a mechanical variable throttle mechanism. Specifically, the constant pressure valve 15 reduces the passage area (that is, the throttle opening) of the refrigerant passage when the pressure of the refrigerant on the outlet side of the air side evaporator 14 falls below a predetermined value, and the outlet of the air side evaporator 14. When the pressure of the refrigerant on the side exceeds a predetermined value, the passage area (that is, the throttle opening) of the refrigerant passage is increased. The gas phase refrigerant whose pressure is adjusted by the constant pressure valve 15 is sucked into the compressor 11 and compressed.

When the fluctuation of the flow rate of the circulating refrigerant circulating in the cycle is small, a fixed throttle made of an orifice, a capillary tube, or the like may be adopted instead of the constant pressure valve 15.

The second expansion valve 16 is a second decompression unit that decompresses and expands the liquid phase refrigerant flowing out of the condenser 12. The second expansion valve 16 is an electric expansion valve. The electric expansion valve is an electric variable throttle mechanism having a valve body configured to change the throttle opening degree and an electric actuator for changing the throttle opening degree. The second expansion valve 16 can completely close the refrigerant flow path.

The second expansion valve 16 is a refrigerant flow switching unit that switches between a state in which the refrigerant flows and a state in which the refrigerant does not flow in the cooling water side evaporator 17. The operation of the second expansion valve 16 is controlled by a control signal output from the control device 60.

The second expansion valve 16 may be a mechanical temperature expansion valve. When the second expansion valve 16 is a mechanical temperature expansion valve, an on-off valve for opening and closing the refrigerant flow path on the second expansion valve 16 side needs to be provided separately from the second expansion valve 16.

The cooling water side evaporator 17 is an evaporating unit that evaporates the refrigerant by exchanging heat between the refrigerant flowing out from the second expansion valve 16 and the cooling water of the low-temperature cooling water circuit 30. In the cooling water side evaporator 17, the refrigerant absorbs heat from the cooling water of the low temperature cooling water circuit 30. The cooling water side evaporator 17 is a heat medium cooler that cools the cooling water of the low temperature cooling water circuit 30. The vapor phase refrigerant evaporated in the cooling water side evaporator 17 is sucked into the compressor 11 and compressed.

The cooling water of the low temperature cooling water circuit 30 is a fluid as a heat medium. The cooling water of the low temperature cooling water circuit 30 is a low temperature heat medium. In this embodiment, as the cooling water of the low temperature cooling water circuit 30, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid is used. The low-temperature cooling water circuit 30 is a low-temperature heat medium circuit in which a low-temperature heat medium circulates. The low temperature cooling water circuit 30 is a second circulation circuit in which the cooling water circulates.

In the high temperature cooling water circuit 20, a condenser 12, a high temperature side pump 21, a heater core 22, a common radiator 45, a reserve tank 24, and an electric heater 25 are arranged.

The high temperature side pump 21 is a heat medium pump that sucks in and discharges cooling water. The high temperature side pump 21 is an electric pump. The high temperature side pump 21 is an electric pump in which the discharge flow rate is constant, but the high temperature side pump 21 may be an electric pump in which the discharge flow rate is variable.

The heater core 22 is an air heating unit that heats the air blown into the vehicle interior by exchanging heat between the cooling water of the high-temperature cooling water circuit 20 and the air blown into the vehicle interior. In the heater core 22, the cooling water dissipates heat to the air blown into the vehicle interior. The heater core 22 is a heat utilization unit that utilizes the heat of the cooling water heated by the condenser 12. The high-temperature cooling water circuit 20 is a heating circuit that circulates cooling water to the heater core 22.

The common radiator 45 is a radiator that exchanges heat between the cooling water of the high-temperature cooling water circuit 20 and the outside air to dissipate heat from the cooling water to the outside air. The common radiator 45 is a radiator common to the high temperature cooling water circuit 20 and the low temperature cooling water circuit 30.

The condenser 12 and the high temperature side pump 21 are arranged in the condenser flow path 20a. The condenser flow path 20a is a flow path through which the cooling water of the high-temperature cooling water circuit 20 flows.

The flow direction of the cooling water in the condenser 12 faces the flow direction of the refrigerant in the condenser 12. That is, in the condenser 12, the cooling water flows in the order of the supercooling portion 12c and the condensing portion 12a.

The heater core 22 is arranged in the heater core flow path 20b. The heater core flow path 20b is a flow path through which the cooling water of the high-temperature cooling water circuit 20 flows.

The common radiator 45 is arranged in the radiator flow path 20c. The radiator flow path 20c is a flow path in which the cooling water of the high-temperature cooling water circuit 20 flows in parallel with the heater core 22.

A first three-way valve 26 is arranged at the branch portion 20d of the high-temperature cooling water circuit 20. The branch portion 20d is a branch portion that branches from the condenser flow path 20a to the heater core flow path 20b and the radiator flow path 20c.

The first three-way valve 26 is a flow path switching unit for switching the flow path of the cooling water in the high temperature cooling water circuit 20. The first three-way valve 26 opens and closes the heater core flow path 20b and the radiator flow path 20c. The first three-way valve 26 adjusts the opening degree of the heater core flow path 20b and the opening degree of the radiator flow path 20c. The first three-way valve 26 adjusts the opening ratio between the heater core flow path 20b and the radiator flow path 20c. The first three-way valve 26 adjusts the flow rate ratio of the cooling water flowing through the heater core 22 and the cooling water flowing through the high temperature side radiator 23.

A reserve tank 24 is arranged at the confluence portion 20e of the high temperature cooling water circuit 20. The merging portion 20e is a merging portion that merges from the heater core flow path 20b and the radiator flow path 20c into the condenser flow path 20a.

The reserve tank 24 is a storage unit for storing excess cooling water. By storing the excess cooling water in the reserve tank 24, it is possible to suppress a decrease in the amount of cooling water circulating in each flow path.

The reserve tank 24 is a closed type reserve tank or an atmosphere open type reserve tank. The closed reserve tank is a reserve tank in which the pressure at the liquid level of the stored cooling water is set to a predetermined pressure. The open-air reserve tank is a reserve tank that makes the pressure at the liquid level of the stored cooling water atmospheric pressure.

The reserve tank 24 has a gas-liquid separation function that separates air bubbles mixed in the cooling water from the cooling water.

The electric heater 25 is arranged on the downstream side of the branch portion 20d of the high temperature cooling water circuit 20 and on the upstream side of the heater core 22. The electric heater 25 is a heat source device that generates Joule heat by supplying electric power from a battery to heat cooling water. The electric heater 25 is a second heat source. The electric heater 25 supplementarily heats the cooling water of the high-temperature cooling water circuit 20. The electric heater 25 is controlled by the control device 60.

A low temperature side pump 31, a cooling water side evaporator 17, and a common radiator 45 are arranged in the low temperature cooling water circuit 30.

The low temperature side pump 31 is a heat medium pump that sucks in and discharges cooling water. The low temperature side pump 31 is an electric pump. The common radiator 45 is an outside air heat absorbing unit that exchanges heat between the cooling water of the low temperature cooling water circuit 30 and the outside air so that the cooling water of the low temperature cooling water circuit 30 absorbs heat from the outside air.

A part of the low temperature cooling water circuit 30 joins the radiator flow path 20c of the high temperature cooling water circuit 20. The common radiator 45 is arranged in a portion of the low-temperature cooling water circuit 30 that joins the radiator flow path 20c of the high-temperature cooling water circuit 20. Therefore, both the cooling water of the radiator flow path 20c of the high-temperature cooling water circuit 20 and the cooling water of the low-temperature cooling water circuit 30 can flow through the common radiator 45.

The common radiator 45 and the outdoor blower 40 are arranged at the front of the vehicle. Therefore, when the vehicle is traveling, the traveling wind can be applied to the common radiator 45.

The outdoor blower 40 is an outside air blower unit that blows outside air toward the common radiator 45. The outdoor blower 40 is an electric blower in which a fan is driven by an electric motor. The operation of the outdoor blower 40 is controlled by the control device 60.

The common radiator 45 and the outdoor blower 40 are arranged at the front of the vehicle. Therefore, when the vehicle is traveling, the traveling wind can be applied to the common radiator 45.

The air-side evaporator 14 and the heater core 22 are housed in the air-conditioning casing 51 of the indoor air-conditioning unit 50. The indoor air conditioning unit 50 is arranged inside an instrument panel (not shown) in the front part of the vehicle interior. The air conditioning casing 51 is an air passage forming member that forms an air passage.

The heater core 22 is arranged on the downstream side of the air flow of the air side evaporator 14 in the air passage in the air conditioning casing 51. An inside / outside air switching box 52 and an indoor blower 53 are arranged in the air conditioning casing 51.

The inside / outside air switching box 52 is an inside / outside air switching unit that switches between inside and outside air and introduces the inside air into the air passage in the air conditioning casing 51. The indoor blower 53 sucks in and blows the inside air and the outside air introduced into the air passage in the air conditioning casing 51 through the inside / outside air switching box 52. The operation of the indoor blower 53 is controlled by the control device 60.

An air mix door 54 is arranged between the air side evaporator 14 and the heater core 22 in the air passage in the air conditioning casing 51. The air mix door 54 adjusts the air volume ratio between the cold air flowing into the heater core 22 and the cold air flowing through the cold air bypass passage 55 among the cold air passing through the air side evaporator 14.

The cold air bypass passage 55 is an air passage through which the cold air that has passed through the air side evaporator 14 vises the heater core 22 and flows.

The air mix door 54 is a rotary door having a rotary shaft rotatably supported with respect to the air conditioning casing 51 and a door substrate portion coupled to the rotary shaft. By adjusting the opening position of the air mix door 54, the temperature of the air conditioning air blown from the air conditioning casing 51 into the vehicle interior can be adjusted to a desired temperature.

The rotating shaft of the air mix door 54 is driven by a servomotor 56. The operation of the servomotor 56 for the air mix door is controlled by the control device 60.

The air mix door 54 may be a slide door that slides and moves in a direction substantially orthogonal to the air flow. The sliding door may be a plate-shaped door formed of a rigid body. It may be a film door made of a flexible film material.

The conditioned air whose temperature is adjusted by the air mix door 54 is blown into the vehicle interior from the air outlet 57 formed in the air-conditioned casing 51.

A heat storage pump 81, a waste heat device 82, a common radiator 45, and a second three-way valve 83 are arranged in the heat storage circuit 80.

The cooling water of the heat storage circuit 80 is a fluid as a heat medium. The cooling water of the heat storage circuit 80 is a high temperature heat medium. In this embodiment, as the cooling water of the heat storage circuit 80, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid is used. The heat storage circuit 80 is a high-temperature heat medium circuit in which a high-temperature heat medium circulates.

The heat storage pump 81 is a heat medium pump that sucks in and discharges cooling water. The heat storage pump 81 is an electric pump.

The waste heat device 82 is a heat source device that generates waste heat as it operates. The waste heat device 82 is the first heat source. For example, the waste heat device 82 is an inverter. The waste heat device 82 may be a motor generator, a charger, or the like. The heat storage pump 81 and the waste heat device 82 are arranged in the waste heat device flow path 80a.

The common radiator 45 is arranged in the defrosting flow path 80b. The defrosting flow path 80b is a flow path through which the cooling water of the heat storage circuit 80 flows. The circulation flow path 80c is a flow path in which the cooling water of the heat storage circuit 80 flows in parallel with the defrosting flow path 80b.

A part of the defrosting flow path 80b joins the radiator flow path 20c of the high temperature cooling water circuit 20 and the low temperature cooling water circuit 30. The common radiator 45 is arranged in a portion of the defrosting flow path 80b that joins the radiator flow path 20c of the high temperature cooling water circuit 20 and the low temperature cooling water circuit 30. Therefore, the cooling water of the radiator flow path 20c of the high temperature cooling water circuit 20, the cooling water of the low temperature cooling water circuit 30, and the cooling water of the defrosting flow path 80b of the heat storage circuit 80 can be circulated to the common radiator 45. It has become.

A second three-way valve 83 is arranged at the branch portion 80d of the heat storage circuit 80. The branch portion 80d is a branch portion that branches from the waste heat equipment flow path 80a into the defrosting flow path 80b and the circulation flow path 80c. The defrosting flow path 80b and the circulation flow path 80c join the waste heat equipment flow path 80a at the merging portion 80e.

The second three-way valve 83 is a flow path switching unit that switches the flow path of the cooling water in the heat storage circuit 80. The second three-way valve 83 opens and closes the defrosting flow path 80b and the circulation flow path 80c. The second three-way valve 83 adjusts the opening degree of the defrosting flow path 80b and the opening degree of the circulation flow path 80c. The second three-way valve 83 adjusts the opening ratio between the defrosting flow path 80b and the circulation flow path 80c. The second three-way valve 83 adjusts the flow rate ratio of the cooling water flowing through the defrosting flow path 80b and the cooling water flowing through the circulation flow path 80c.

The control device 60 shown in FIG. 2 is composed of a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof. The control device 60 performs various operations and processes based on the control program stored in the ROM. Various controlled devices are connected to the output side of the control device 60. The control device 60 is a control unit that controls the operation of various controlled devices.

The controlled devices controlled by the control device 60 are the compressor 11, the first expansion valve 13, the second expansion valve 16, the first three-way valve 26, the outdoor blower 40, the indoor blower 53, the servomotor 56 for the air mix door, and the like. The second three-way valve 83 and the like.

The software and hardware for controlling the electric motor of the compressor 11 in the control device 60 is a refrigerant discharge capacity control unit. The software and hardware for controlling the first expansion valve 13 and the second expansion valve 16 in the control device 60 are throttle control units.

The software and hardware for controlling the first three-way valve 26 and the second three-way valve 83 of the control device 60 is a three-way valve control unit. The control device 60, the first three-way valve 26, and the second three-way valve 83 are flow path switching portions for switching the flow path of the cooling water.

The software and hardware for controlling the outdoor blower 40 among the control devices 60 is an outside air blower capacity control unit.

The software and hardware for controlling the indoor blower 53 among the control devices 60 is an air blower capacity control unit.

The software and hardware for controlling the air mix door servomotor 56 among the control devices 60 are air volume ratio control units.

Various control sensor groups are connected to the input side of the control device 60. Various control sensor groups include an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation amount sensor 63, a high temperature cooling water temperature sensor 64, a radiator temperature sensor 65, a heat storage cooling water temperature sensor 66, and the like.

The inside air temperature sensor 61 detects the vehicle interior temperature Tr. The outside air temperature sensor 62 detects the outside air temperature Tam. The solar radiation amount sensor 63 detects the solar radiation amount Ts in the vehicle interior.

The high temperature cooling water temperature sensor 64 detects the temperature TWH of the cooling water of the high temperature cooling water circuit 20. For example, the high temperature cooling water temperature sensor 64 detects the temperature of the cooling water flowing out from the electric heater 25.

The radiator temperature sensor 65 detects the temperature TWR of the cooling water flowing into the common radiator 45. The heat storage cooling water temperature sensor 66 detects the temperature TWW of the cooling water of the heat storage circuit 80. For example, the heat storage cooling water temperature sensor 66 detects the temperature of the cooling water flowing out of the waste heat device 82.

Various operation switches (not shown) are connected to the input side of the control device 60. Various operation switches are provided on the operation panel 70 and are operated by an occupant. The operation panel 70 is arranged near the instrument panel in the front part of the vehicle interior. Operation signals from various operation switches are input to the control device 60.

Various operation switches are an auto switch, an air conditioner switch, a temperature setting switch, and the like. The auto switch is a switch for setting and canceling the automatic control operation of the vehicle air conditioner 1. The air conditioner switch is a switch for setting whether or not to cool the air in the indoor air conditioning unit 50. The temperature setting switch is a switch for setting the set temperature in the vehicle interior.

Next, the operation in the above configuration will be described. In the following, the control device 60 describes the operation when the auto switch of the operation panel 70 is turned on by the occupant. When the air conditioner switch of the operation panel 70 is turned on by the occupant, the operation mode is switched based on the target blowout temperature TAO or the like and the control map shown in FIG. The operation mode includes at least a cooling mode and a dehumidifying / heating mode.

The target blowing temperature TAO is the target temperature of the blowing air blown into the vehicle interior. The control device 60 calculates the target blowout temperature TAO based on the following mathematical formula.

TAO = Kset x Tset-Kr x Tr-Kam x Tam-Ks x Ts + C
In this formula, Tset is the vehicle interior set temperature set by the temperature setting switch of the operation panel 70, Tr is the inside air temperature detected by the inside air temperature sensor 61, Tam is the outside air temperature detected by the outside air temperature sensor 62, and Ts is. It is the amount of solar radiation detected by the solar radiation amount sensor 63. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

In the low temperature range of the target blowout temperature TAO, switch to the cooling mode. In the high temperature range of the target blowout temperature TAO, switch to the dehumidifying heating mode.

In the dehumidifying / heating mode, the air blown into the vehicle interior is cooled and dehumidified by the air side evaporator 14, and the air cooled and dehumidified by the air side evaporator 14 is heated by the heater core 22 to dehumidify and heat the vehicle interior.

The control device 60 switches to the heating mode when the air conditioner switch of the operation panel 70 is turned off by the occupant and the target blowout temperature TAO is in the high temperature range.

In the heating mode, the interior of the vehicle is heated by heating the air blown into the vehicle interior with the heater core 22 without cooling and dehumidifying with the air-side evaporator 14.

Next, the operation in the cooling mode, the dehumidifying heating mode, and the heating mode will be described. In the cooling mode, the dehumidifying heating mode, and the heating mode, the control device 60 operates the various control devices connected to the control device 60 (in other words, in other words) based on the target blowout temperature TAO, the detection signal of the above-mentioned sensor group, and the like. , Control signals to be output to various control devices) are determined.

(1) Cooling mode In the cooling mode, the control device 60 operates the compressor 11, the high temperature side pump 21, and the heat storage pump 81, and stops the low temperature side pump 31. In the cooling mode, the control device 60 opens the first expansion valve 13 at the throttle opening and closes the second expansion valve 16. In the cooling mode, the control device 60 controls the first three-way valve 26 so that both the heater core flow path 20b and the radiator flow path 20c are open, and the defrosting flow path 80b is closed to open the circulation flow path 80c. 2 Controls the three-way valve 83.

As a result, in the refrigerating cycle device 10 in the cooling mode, the refrigerant flows as follows. That is, the high-pressure refrigerant discharged from the compressor 11 flows into the condenser 12. The refrigerant that has flowed into the condenser 12 dissipates heat to the cooling water of the high-temperature cooling water circuit 20. As a result, the refrigerant is cooled and condensed in the condenser 12.

The refrigerant flowing out of the condenser 12 flows into the first expansion valve 13 and is decompressed and expanded by the first expansion valve 13 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the first expansion valve 13 flows into the air-side evaporator 14 and absorbs heat from the air blown into the vehicle interior to evaporate. As a result, the air blown into the vehicle interior is cooled.

Then, the refrigerant flowing out of the air-side evaporator 14 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

As described above, in the cooling mode, the low-pressure refrigerant is made to absorb heat from the air by the air-side evaporator 14, and the cooled air can be blown out into the vehicle interior. As a result, it is possible to realize cooling in the vehicle interior.

In the high-temperature cooling water circuit 20 in the cooling mode, the cooling water of the high-temperature cooling water circuit 20 circulates in the common radiator 45, and the high-temperature side radiator 23 dissipates heat from the cooling water to the outside air.

At this time, the cooling water of the high-temperature cooling water circuit 20 also circulates in the heater core 22, but the amount of heat dissipated from the cooling water to the air in the heater core 22 is adjusted by the air mix door 54.

Regarding the control signal output to the servomotor of the air mix door 54, it is determined that the conditioned air temperature adjusted by the air mix door 54 becomes the target blowout temperature TAO. Specifically, the opening degree of the air mix door 54 is determined based on the target outlet temperature TAO, the temperature of the air-side evaporator 14, the temperature TW of the cooling water of the high-temperature cooling water circuit 20, and the like.

In the heat storage circuit 80 in the cooling mode, the cooling water circulates in the waste heat device 82, and the waste heat of the waste heat device 82 is stored in the cooling water.

(2) Dehumidifying / heating mode In the dehumidifying / heating mode, the control device 60 operates the compressor 11, the high temperature side pump 21, the low temperature side pump 31, and the heat storage pump 81. In the dehumidifying / heating mode, the control device 60 opens the first expansion valve 13 and the second expansion valve 16 at the throttle opening. In the dehumidifying / heating mode, the control device 60 controls the first three-way valve 26 so that the heater core flow path 20b opens and the radiator flow path 20c closes, and the defrosting flow path 80b closes and the circulation flow path 80c opens. The second three-way valve 83 is controlled.

In the refrigerating cycle device 10 in the dehumidifying / heating mode, the refrigerant flows as follows. That is, in the refrigerating cycle device 10, as shown by the thick solid line in FIG. 4, the high-pressure refrigerant discharged from the compressor 11 flows into the condenser 12 and exchanges heat with the cooling water of the high-temperature cooling water circuit 20. Dissipate heat. As a result, the cooling water of the high-temperature cooling water circuit 20 is heated.

The refrigerant flowing out of the condenser 12 flows into the first expansion valve 13 and is decompressed and expanded by the first expansion valve 13 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the first expansion valve 13 flows into the air-side evaporator 14 and absorbs heat from the air blown into the vehicle interior to evaporate. As a result, the air blown into the vehicle interior is cooled and dehumidified.

Then, the refrigerant flowing out of the air-side evaporator 14 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

At the same time, in the refrigeration cycle device 10, the refrigerant flowing out of the condenser 12 flows into the second expansion valve 16 and is decompressed and expanded by the second expansion valve 16 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the cooling water side evaporator 17 and absorbs heat from the cooling water of the low-temperature cooling water circuit 30 to evaporate. As a result, the cooling water of the low temperature cooling water circuit 30 is cooled.

Then, the refrigerant flowing out of the cooling water side evaporator 17 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

In the high-temperature cooling water circuit 20 in the dehumidifying and heating mode, the cooling water circulates between the condenser 12 and the heater core 22, but the cooling water does not circulate to the high-temperature side radiator 23.

Regarding the control signal output to the servomotor of the air mix door 54, the air mix door 54 is located at the solid line position in FIG. 4, the air passage of the heater core 22 is fully opened, and the blown air that has passed through the air side evaporator 14 is used. The total flow rate is determined to pass through the heater core 22.

As a result, the heater core 22 dissipates heat from the cooling water of the high-temperature cooling water circuit 20 to the air blown into the vehicle interior. Therefore, the air cooled and dehumidified by the air-side evaporator 14 is heated by the heater core 22 and blown out into the vehicle interior.

At this time, since the first three-way valve 26 closes the radiator flow path 20c, the cooling water of the high-temperature cooling water circuit 20 does not circulate in the common radiator 45. Therefore, the common radiator 45 does not dissipate heat from the cooling water to the outside air.

In the low-temperature cooling water circuit 30 in the dehumidifying / heating mode, the cooling water of the low-temperature cooling water circuit 30 circulates in the common radiator 45, and the cooling water of the low-temperature cooling water circuit 30 absorbs heat from the outside air in the common radiator 45.

As described above, in the dehumidifying / heating mode, the heat of the high-pressure refrigerant discharged from the compressor 11 is radiated to the cooling water of the high-temperature cooling water circuit 20 by the condenser 12, and the heat of the cooling water of the high-temperature cooling water circuit 20 is dissipated. Can be radiated to the air by the heater core 22 and the air heated by the heater core 22 can be blown out into the vehicle interior.

In the heater core 22, the air cooled and dehumidified by the air side evaporator 14 is heated. This makes it possible to realize dehumidifying and heating in the vehicle interior.

In the heat storage circuit 80 in the dehumidifying / heating mode, the cooling water circulates in the waste heat device 82, and the waste heat of the waste heat device 82 is stored in the cooling water.

(3) Heating mode In the heating mode, the control device 60 operates the compressor 11, the high temperature side pump 21, the low temperature side pump 31, and the heat storage pump 81. In the heating mode, the control device 60 closes the first expansion valve 13 and opens the second expansion valve 16 at the throttle opening. In the heating mode, the control device 60 controls the first three-way valve 26 so that the heater core flow path 20b opens and the radiator flow path 20c closes, and the second defrosting flow path 80b closes and the circulation flow path 80c opens. Controls the three-way valve 83.

In the refrigerating cycle device 10 in the heating mode, the refrigerant flows as follows. That is, in the refrigeration cycle device 10, the refrigerant flowing out of the condenser 12 flows into the second expansion valve 16 and is decompressed and expanded by the second expansion valve 16 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the cooling water side evaporator 17 and absorbs heat from the cooling water of the low-temperature cooling water circuit 30 to evaporate. As a result, the cooling water of the low temperature cooling water circuit 30 is cooled.

At this time, since the first expansion valve 13 is closed, the refrigerant does not flow to the air side evaporator 14. Therefore, the air is not cooled and dehumidified by the air side evaporator 14.

In the high-temperature cooling water circuit 20 in the heating mode, the cooling water circulates between the condenser 12 and the heater core 22, but the cooling water does not circulate to the high-temperature side radiator 23.

Regarding the control signal output to the servomotor of the air mix door 54, the air mix door 54 is located at the solid line position in FIG. 5, the air passage of the heater core 22 is fully opened, and the blown air that has passed through the air side evaporator 14 is used. The total flow rate is determined to pass through the heater core 22.

As a result, the heater core 22 dissipates heat from the cooling water of the high-temperature cooling water circuit 20 to the air blown into the vehicle interior. Therefore, the air that has passed through the air-side evaporator 14 (that is, the air that has not been cooled and dehumidified by the air-side evaporator 14) is heated by the heater core 22 and blown out into the vehicle interior.

At this time, since the first three-way valve 26 closes the radiator flow path 20c, the cooling water of the high-temperature cooling water circuit 20 does not circulate in the common radiator 45. Therefore, the common radiator 45 does not dissipate heat from the cooling water to the outside air.

In the low-temperature cooling water circuit 30 in the heating mode, the cooling water of the low-temperature cooling water circuit 30 circulates in the common radiator 45, and the cooling water of the low-temperature cooling water circuit 30 absorbs heat from the outside air in the common radiator 45.

As described above, in the heating mode, the heat of the high-pressure refrigerant discharged from the compressor 11 is radiated to the cooling water of the high-temperature cooling water circuit 20 by the condenser 12, and the heat of the cooling water of the high-temperature cooling water circuit 20 is dissipated. The heater core 22 can dissipate heat to the air, and the air heated by the heater core 22 can be blown out into the vehicle interior.

The heater core 22 heats the air that has passed through the air-side evaporator 14 without being cooled and dehumidified by the air-side evaporator 14. As a result, it is possible to realize heating in the vehicle interior.

In the heat storage circuit 80 in the heating mode, the cooling water circulates in the waste heat device 82, and the waste heat of the waste heat device 82 is stored in the cooling water.

(4) Defrosting mode In the defrosting mode, the common radiator 45 is defrosted after the dehumidifying heating mode or the heating mode. In the dehumidifying heating mode or the heating mode, the cooling water of the low-temperature cooling water circuit 30 absorbs heat from the outside air in the common radiator 45, so that frost is formed on the common radiator 45 when the temperature of the common radiator 45 becomes below the freezing point. Therefore, when frost is formed on the common radiator 45, the defrosting mode is executed to defrost the common radiator 45.

The defrosting mode includes a waste heat defrosting mode and a heating heat defrosting mode. In the waste heat defrosting mode, the waste heat of the waste heat device 82 is used to defrost the common radiator 45. In the heating defrosting mode, the heat generated for heating is used to defrost the common radiator 45.

(4-1) Waste heat defrosting mode In the waste heat defrosting mode, the control device 60 operates the heat storage pump 81 and stops the compressor 11, the low temperature side pump 31, the outdoor blower 40, and the indoor blower 53. In the dehumidifying / heating mode, the control device 60 controls the first three-way valve 26 so as to open the heater core flow path 20b and close the radiator flow path 20c, and opens the dehumidifying flow path 80b to close the circulation flow path 80c. The second three-way valve 83 is controlled.

Since the compressor 11 is stopped, no refrigerant flows through the refrigeration cycle device 10 in the defrosting mode. Since the low temperature side pump 31 is stopped, the cooling water does not circulate in the low temperature cooling water circuit 30 in the defrosting mode.

In the heat storage circuit 80 in the waste heat defrosting mode, as shown by the thick solid line in FIG. 3, the cooling water of the heat storage circuit 80 circulates between the waste heat device 82 and the common radiator 45.

Specifically, the cooling water discharged from the heat storage pump 81 passes through the waste heat device 82, flows through the common radiator 45, and is sucked into the high temperature side pump 21. As a result, the high-temperature cooling water heated by the waste heat device 82 flows into the common radiator 45.

Since the outdoor blower 40 is stopped, air does not flow to the common radiator 45. Therefore, in the common radiator 45, the cooling water is not cooled by the outside air.

In this way, the heat of the cooling water of the heat storage circuit 80 flowing through the common radiator 45 can melt the frost adhering to the surface of the common radiator 45. That is, the waste heat of the waste heat device 82 can be effectively used for defrosting.

(4-2) Heating heat defrosting mode In the heating heat defrosting mode, the control device 60 operates the high temperature side pump 21 and the heat storage pump 81, and operates the compressor 11, the low temperature side pump 31, the outdoor blower 40 and the indoor blower. Stop 53. In the dehumidifying / heating mode, the control device 60 controls the first three-way valve 26 so as to open both the heater core flow path 20b and the radiator flow path 20c, closes the dehumidification flow path 80b, and opens the circulation flow path 80c. The second three-way valve 83 is controlled.

Since the compressor 11 is stopped, no refrigerant flows through the refrigeration cycle device 10 in the defrosting mode. Since the low temperature side pump 31 is stopped, the cooling water does not circulate in the low temperature cooling water circuit 30 in the defrosting mode.

In the high-temperature cooling water circuit 20 in the heating heat defrost mode, as shown by the thick solid line in FIG. 4, the cooling water of the high-temperature cooling water circuit 20 is located between the condenser 12, the heater core 22, the electric heater 25, and the common radiator 45. Circulates.

Specifically, the cooling water discharged from the high temperature side pump 21 passes through the condenser 12 and branches to the heater core 22 side and the common radiator 45 side at the branch portion 20d, and the heater core 22 and the electric heater 25 and the common radiator 45. Are flowed in parallel and merged at the merging portion 20e, and are sucked into the high temperature side pump 21. As a result, the high-temperature cooling water in the condenser 12 flows into the common radiator 45.

Since the indoor blower 53 is stopped, air does not flow to the heater core 22. Therefore, the high-temperature cooling water in the heater core 22 flows into the common radiator 45 without being cooled by air.

Since the outdoor blower 40 is stopped, air does not flow to the common radiator 45. Therefore, in the common radiator 45, the cooling water is not cooled by the outside air.

In this way, the heat of the cooling water of the high-temperature cooling water circuit 20 flowing through the common radiator 45 can melt the frost adhering to the surface of the common radiator 45.

The cooling water cooled by the common radiator 45 merges with the cooling water flowing out from the heater core 22 at the confluence portion 20e, and then flows into the condenser 12.

By circulating the cooling water in this way, the heat of the cooling water heated by the condenser 12 can be effectively used for defrosting. When the heat of the cooling water heated by the condenser 12 is insufficient for the heat required for defrosting, the heat generated by the electric heater 25 can be used for defrosting.

In the heat storage circuit 80 in the heating heat defrost mode, as shown by the thick solid line in FIG. 4, the cooling water circulates in the waste heat device 82 and the waste heat of the waste heat device 82 is stored in the cooling water.

The control device 60 switches between the waste heat defrosting mode and the heating heat defrosting mode by executing the control process shown in the flowchart of FIG.

In step S100, it is determined whether or not the ignition switch (that is, the start switch of the vehicle system) is turned on and the air conditioning is turned on. For example, when the auto switch or the air conditioner switch of the operation panel 70 is turned on, it is determined that the air conditioner is turned on.

If it is determined in step S100 that the ignition switch is turned on and the air conditioning is turned on, the process proceeds to step S110. If it is not determined in step S100 that the ignition switch is turned on and the air conditioning is turned on, the process proceeds to step S200.

In step S110, it is determined whether or not the common radiator 45 is frosted and the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1. For example, whether or not the common radiator 45 is frosted is determined by using the control characteristic diagram shown in FIG. 6 based on the temperature TWR of the cooling water flowing into the common radiator 45 and the outside air temperature Tam.

That is, when the difference between the outside air temperature Tam and the temperature TWR of the cooling water flowing into the common radiator 45 is large, it is determined that the common radiator 45 is frosted. When the common radiator 45 is frosted, the performance of the common radiator 45 deteriorates, so that the control device 60 increases the rotation speed of the compressor 11 to reduce the low pressure of the cycle in order to secure the required heat absorption amount. .. When the low pressure of the cycle decreases, the temperature of the cooling water cooled by the cooling water side evaporator 17 (that is, the temperature TWR of the cooling water flowing into the common radiator 45) decreases. Therefore, when the difference between the outside air temperature Tam and the temperature TWR of the cooling water flowing into the common radiator 45 is large, it can be estimated that the common radiator 45 is frosted.

The waste heat defrosting temperature α1 is the temperature (predetermined temperature) of the cooling water capable of melting the frost adhering to the surface of the common radiator 45, and is stored in advance in the control device 60.

If the common radiator 45 is frosted in step S110 and it is not determined that the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1, the process proceeds to step S120. If it is determined in step S110 that the common radiator 45 is frosted and the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1, the process proceeds to step S130.

In step S120, it is determined whether or not the common radiator 45 is frosted and the ignition switch is turned off. If it is determined in step S120 that the common radiator 45 is frosted and the ignition switch is turned off, the process proceeds to step S130. If it is determined in step S120 that the common radiator 45 is frosted and the ignition switch is not turned off, the process returns to step S100.

In step S130, the mode is switched to the waste heat defrosting mode, and the process proceeds to step S140.

In step S140, it is determined whether or not the common radiator 45 is frosted and the temperature TWH of the cooling water of the high-temperature cooling water circuit 20 exceeds the heating heat defrosting temperature α2. The heating heat defrosting temperature α2 is the temperature (predetermined temperature) of the cooling water capable of melting the frost adhering to the surface of the common radiator 45, and is stored in advance in the control device 60.

If the common radiator 45 is frosted in step S140 and it is not determined that the temperature TWH of the cooling water of the high temperature cooling water circuit 20 exceeds the heating heat defrosting temperature α2, the process proceeds to step S150. If it is determined in step S140 that the common radiator 45 is frosted and the temperature TWH of the cooling water of the high temperature cooling water circuit 20 exceeds the heating heat defrosting temperature α2, the process proceeds to step S160.

In step S150, it is determined whether or not the common radiator 45 is frosted and the ignition switch is turned off. If it is determined in step S150 that the common radiator 45 is frosted and the ignition switch is turned off, the process proceeds to step S160. If it is determined in step S150 that the common radiator 45 is frosted and the ignition switch is not turned off, the process returns to step S100. In step S160, the mode is switched to the heating heat defrosting mode and the process returns to step S100.

In step S200, it is determined whether or not the pre-air conditioning is turned on. Pre-air conditioning is an air-conditioning operation that is started before the occupant gets in (in other words, when the ignition switch is OFF). The pre-air conditioning is executed by the occupant storing the target temperature Tset in the vehicle interior, the pre-air conditioning start time, and the like in the control device 60 by the operation panel 70 or the remote control terminal.

If it is determined in step S200 that the pre-air conditioning is turned on, the process proceeds to step S210. If it is not determined in step S200 that the pre-air conditioning is turned on, the process returns to step S100.

In step S210, it is determined whether or not the common radiator 45 is frosted and the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1. For example, the temperature TWR of the cooling water flowing into the common radiator 45 and the outside air temperature Tam are compared to determine whether or not the common radiator 45 is frosted.

If the common radiator 45 is frosted in step S210 and it is not determined that the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1, the process proceeds to step S220. If it is determined in step S210 that the common radiator 45 is frosted and the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1, the process proceeds to step S230.

In step S220, it is determined whether or not the common radiator 45 is frosted and the pre-air conditioning is turned off. If it is determined in step S220 that the common radiator 45 is frosted and the pre-air conditioning is turned off, the process proceeds to step S230. If it is determined in step S120 that the common radiator 45 is frosted and the pre-air conditioning is not turned off, the process returns to step S100.

In step S230, the mode is switched to the waste heat defrosting mode, and the process proceeds to step S240.

In step S240, it is determined whether or not the common radiator 45 is frosted and the temperature TWH of the cooling water of the high temperature cooling water circuit 20 exceeds the heating heat defrosting temperature α2.

If the common radiator 45 is frosted in step S240 and it is not determined that the temperature TWH of the cooling water of the high temperature cooling water circuit 20 exceeds the heating heat defrosting temperature α2, the process proceeds to step S250. If it is determined in step S240 that the common radiator 45 is frosted and the temperature TWH of the cooling water of the high temperature cooling water circuit 20 exceeds the heating heat defrosting temperature α2, the process proceeds to step S260.

In step S250, it is determined whether or not the common radiator 45 is frosted and the pre-air conditioning is turned off. If it is determined in step S250 that the common radiator 45 is frosted and the pre-air conditioning is turned off, the process proceeds to step S260. If it is determined in step S250 that the common radiator 45 is frosted and the pre-air conditioning is not turned off, the process returns to step S100. In step S260, the mode is switched to the heating heat defrosting mode and the process returns to step S100.

FIG. 7 is a time chart showing an example of the control result of the present embodiment. FIG. 7 shows the coefficient of performance (so-called COP) or the time transition of the performance of the refrigerating cycle device 10 when the waste heat defrosting mode is executed during running, stopping, and pre-air conditioning. As the frost formation progresses on the common radiator 45, the coefficient of performance or performance deteriorates, but by executing the waste heat defrosting mode, the common radiator 45 is defrosted and the coefficient of performance or performance is restored.

FIG. 8 shows the coefficient of performance (so-called COP) or the time transition of the performance of the refrigerating cycle apparatus 10 when the waste heat defrosting mode is switched to the heating heat defrosting mode. Since defrosting can be continued by the heating heat defrosting mode even if the waste heat defrosting mode cannot be completely defrosted, the coefficient of performance or performance can be restored to a higher level than when only the waste heat defrosting mode is executed. ..

In the present embodiment, the control device 60 determines whether or not defrosting of the common radiator 45 is necessary. When it is determined that defrosting of the common radiator 45 is not necessary, the cooling water is circulated separately in the heat storage circuit 80, the high temperature cooling water circuit 20 and the low temperature cooling water circuit 30. When it is determined that defrosting of the common radiator 45 is necessary, the first three-way valve 26 or the second three-way valve is controlled so that the cooling water of the heat storage circuit 80 or the high-temperature cooling water circuit 20 is circulated to the common radiator 45.

According to this, defrosting can be reliably performed when defrosting of the common radiator 45 is required, so that defrosting can be efficiently performed.

In the present embodiment, in the heat storage circuit 80, the waste heat of the waste heat device 82 is stored in the cooling water by circulating the cooling water in the waste heat device 82. According to this, since waste heat can be effectively used for defrosting, defrosting can be performed with energy saving.

In the present embodiment, when the control device 60 determines that defrosting of the common radiator 45 is necessary, the cooling water of the high temperature cooling water circuit 20 flows in parallel with the heater core 22 and the common radiator 45 on the first three sides. Controls the valve 26 or the second three-way valve.

According to this, since a part of the heating heat can be used for defrosting, defrosting can be reliably performed.

In the present embodiment, when the control device 60 determines that defrosting of the common radiator 45 is necessary, the first three-way valve 26 or the second three-way valve so as to circulate the cooling water of the heat storage circuit 80 to the common radiator 45. To control. When the control device 60 determines that defrosting of the common radiator 45 is necessary after circulating the cooling water of the heat storage circuit 80 to the common radiator 45, the cooling water of the high temperature cooling water circuit 20 is the heater core 22 and the common radiator. The first three-way valve 26 or the second three-way valve is controlled so as to flow in parallel with 45.

According to this, when the defrost cannot be completely defrosted by the waste heat, the defrosting is performed by the heating heat, so that the defrosting can be performed with energy saving and surely.

In the present embodiment, in the control device 60, when the vehicle is traveling, the common radiator 45 is in a frosted state, and the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1. , Or the temperature TWH of the cooling water of the high-temperature cooling water circuit 20 is higher than the heating heat defrosting temperature α2, and it is determined that defrosting of the common radiator 45 is necessary.

As a result, it can be appropriately determined that defrosting of the common radiator 45 is necessary, so that defrosting can be performed efficiently.

In the present embodiment, in the control device 60, when the pre-air conditioning is performed, the common radiator 45 is in a frosted state, and the temperature TWW of the cooling water of the heat storage circuit 80 exceeds the waste heat defrosting temperature α1. , Or the temperature TWH of the cooling water of the high temperature cooling water circuit 20 is higher than the heating heat defrosting temperature α2, and it is determined that defrosting of the common radiator 45 is necessary. As a result, defrosting can be performed without impairing the comfort of air conditioning for the occupants as much as possible.

In the present embodiment, the control device 60 determines that defrosting of the common radiator 45 is necessary when the common radiator 45 is in the frosted state when the vehicle changes from the traveling state to the stopped state.

As a result, defrosting can be performed by effectively utilizing the remaining heat generated while the vehicle is running, so that defrosting can be performed with energy saving.

In the present embodiment, the control device 60 determines that defrosting of the common radiator 45 is necessary when the common radiator 45 is in a frosted state when the pre-air conditioning is completed.

As a result, defrosting can be performed by effectively utilizing the remaining heat generated for air conditioning before the occupant gets into the vehicle, so that defrosting can be performed with energy saving.

In the present embodiment, the control device 60 determines whether or not the common radiator 45 is in a frosted state based on the temperature TWR of the cooling water flowing through the common radiator 45 and the temperature Tam of the outside air. This makes it possible to accurately determine the frost formation state with simple control.

(Second Embodiment)
In the first embodiment, the radiator flow path 20c of the high temperature cooling water circuit 20, the low temperature cooling water circuit 30, and the defrosting flow path 80b of the heat storage circuit 80 are merged, and the common radiator 45 is arranged at the merged portion. ing. In the present embodiment, as shown in FIG. 9, the radiator flow path 20c of the high temperature cooling water circuit 20 does not merge with the defrosting flow path 80b of the low temperature cooling water circuit 30 and the heat storage circuit 80, and the common radiator 45 is used. It has a high temperature side radiator 23 arranged in the radiator flow path 20c of the high temperature cooling water circuit 20, and a low temperature side radiator 32 arranged in a confluence portion between the low temperature cooling water circuit 30 and the defrosting flow path 80b. ..

The low temperature side radiator 32 is a first heat medium distribution unit of the common radiator 45, and the high temperature side radiator 23 is a second heat medium distribution unit of the common radiator 45.

The high temperature side radiator 23 is a radiator that exchanges heat between the cooling water of the high temperature cooling water circuit 20 and the outside air to dissipate heat from the cooling water to the outside air. The low-temperature side radiator 32 is an outside air heat absorbing unit that exchanges heat between the cooling water of the low-temperature cooling water circuit 30 and the outside air so that the cooling water of the low-temperature cooling water circuit 30 absorbs heat from the outside air. The high temperature side radiator 23 and the low temperature side radiator 32 are joined to each other by a common fin 37.

The common fin 37 is a heat exchange promoting member that promotes heat exchange between the cooling water and air. The common fin 37 is a member made of metal (for example, made of aluminum). The common fin 37 is a coupling portion that transfers heat from the high temperature side radiator 23 to the low temperature side radiator 32 by bonding the high temperature side radiator 23 and the low temperature side radiator 32 with a metal. The common fin 37 is a heat transfer member that connects the high temperature side radiator 23 and the low temperature side radiator 32 so as to be heat transferable.

The high temperature side radiator 23 and the low temperature side radiator 32 are arranged in series in this order in the flow direction of the outside air. Outside air is blown to the high temperature side radiator 23 and the low temperature side radiator 32 by the outdoor blower 40.

In the cooling mode, the control device 60 controls the first three-way valve 26 so that both the heater core flow path 20b and the radiator flow path 20c are open. As a result, in the cooling mode, the cooling water of the high-temperature cooling water circuit 20 circulates in the high-temperature side radiator 23, and the high-temperature side radiator 23 dissipates heat from the cooling water to the outside air.

In the dehumidifying / heating mode, the control device 60 controls the first three-way valve 26 so that the heater core flow path 20b opens and the radiator flow path 20c closes. As a result, in the dehumidifying / heating mode, the cooling water of the low-temperature cooling water circuit 30 absorbs heat from the outside air in the low-temperature side radiator 32.

In the heating mode, the control device 60 controls the first three-way valve 26 so that the heater core flow path 20b opens and the radiator flow path 20c closes. As a result, in the heating mode, the cooling water of the low-temperature cooling water circuit 30 absorbs heat from the outside air at the low-temperature side radiator 32.

In the waste heat defrosting mode, the control device 60 stops the low temperature side pump 31 and controls the second three-way valve 83 so that the cooling water of the waste heat equipment flow path 80a of the heat storage circuit 80 flows to the low temperature side radiator 32. do. As a result, the frost adhering to the surface of the low temperature radiator 32 can be melted by the heat of the cooling water of the heat storage circuit 80 flowing through the low temperature radiator 32.

In the heating heat defrost mode, the control device 60 stops the low temperature side pump 31, and as shown by the thick line arrow in FIG. 10, the cooling water in the radiator flow path 20c of the high temperature cooling water circuit 20 flows to the high temperature side radiator 23. The first three-way valve 26 is controlled so as to do so.

Since the high temperature side radiator 23 and the low temperature side radiator 32 are connected to each other by a common fin 37 so as to be heat transferable to each other, the heat of the cooling water of the high temperature cooling water circuit 20 flowing through the high temperature side radiator 23 is low temperature through the fin 37. Move to the side radiator 32.

The heat supplied to the low temperature radiator 32 in this way can melt the frost adhering to the surface of the low temperature radiator 32.

In the present embodiment, the common radiator 45 includes a low-temperature side radiator 32 through which the cooling water cooled by the cooling water-side evaporator 17 flows, a high-temperature side radiator 23 through which the cooling water heated by the electric heater 25 flows, and a low-temperature side radiator. It has fins 37 that connect the 32 and the high temperature side radiator 23 so as to be heat transferable.

As a result, the cooling water cooled by the cooling water side evaporator 17 and the cooling water heated by the electric heater 25 can be defrosted without being mixed, so that the cooling water having different temperature zones can be efficiently managed.

(Third Embodiment)
In the above embodiment, when the defrosting cannot be completely performed in the waste heat defrosting mode, the waste heat defrosting mode is shifted to the heating heat defrosting mode to improve the defrosting ability. However, in the present embodiment, FIG. 11 shows. As such, defrost only in the heating heat defrost mode without executing the waste heat defrost mode.

The flowchart of the present embodiment shown in FIG. 11 is obtained by deleting the step related to the waste heat heating mode from the flowchart of the first embodiment shown in FIG.

FIG. 12 shows the coefficient of performance (so-called COP) or the time transition of the performance of the refrigerating cycle device 10 when the heating heat defrosting mode is executed during running, stopping, and pre-air conditioning. Since a part of the heating heat is spent for defrosting instead of heating, the coefficient of performance or performance is temporarily deteriorated, but the coefficient of performance or performance is restored by defrosting the common radiator 45.

(Other embodiments)
The above embodiments can be combined as appropriate. The above embodiment can be variously modified as follows, for example.

(1) In the above embodiment, cooling water is used as the heat medium, but various media such as oil may be used as the heat medium. A nanofluid may be used as the heat medium. The nanofluid is a fluid in which nanoparticles having a particle size on the order of nanometers are mixed.

(2) In the refrigerating cycle apparatus 10 of the above embodiment, a fluorocarbon-based refrigerant is used as the refrigerant, but the type of the refrigerant is not limited to this, and a natural refrigerant such as carbon dioxide, a hydrocarbon-based refrigerant, or the like can be used. You may use it.

Further, the refrigeration cycle apparatus 10 of the above embodiment constitutes a subcritical refrigeration cycle in which the high pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant, but the supercritical refrigeration cycle in which the high pressure side refrigerant pressure exceeds the critical pressure of the refrigerant. May be configured.

(3) In the third embodiment, the high temperature side radiator 23 and the low temperature side radiator 32 are separate radiators, and the high temperature side radiator 23 and the low temperature side radiator 32 are joined to each other by a common fin 37. However, the high temperature side radiator 23 and the low temperature side radiator 32 may be composed of one radiator.

For example, even if the high temperature side radiator 23 and the low temperature side radiator 32 are configured by one radiator by integrating the cooling water tank of the high temperature side radiator 23 and the cooling water tank of the low temperature side radiator 32 with each other. good.

(4) In the above embodiment, the electric heater 25 is arranged on the downstream side of the branch portion 20d of the high temperature cooling water circuit 20 and on the upstream side of the heater core 22, but the position of the electric heater 25 in the high temperature cooling water circuit 20 is this. Not limited to.

For example, the electric heater 25 may be arranged on the downstream side of the condenser 12 of the high temperature cooling water circuit 20 and on the upstream side of the branch portion 20d. In this case, the heater core flow path 20b may be closed by the first three-way valve 26 in the heating heat defrosting mode to stop the cooling water flow in the heater core flow path 20b.

11 Compressor 12 Condenser (heat dissipation part)
16 Second expansion valve (pressure reducing part)
17 Cooling water side evaporator (evaporation part)
20 High-temperature cooling water circuit (first circulation circuit, heating circuit)
25 Electric heater (heat source, second heat source)
26 1st three-way valve (flow path switching part)
30 Low temperature cooling water circuit (second circulation circuit)
45 Common radiator (outside air heat absorbing part)
60 Control device (flow path switching unit)
80 Heat storage circuit (1st circulation circuit, heat storage circuit)
82 Waste heat equipment (heat source, first heat source)
83 Second three-way valve (flow path switching part)

Claims (10)

A compressor (11) that sucks in the refrigerant, compresses it, and discharges it.
A heat radiating unit (12) that dissipates heat from the refrigerant discharged from the compressor, and
A decompression unit (16) that depressurizes the refrigerant radiated by the heat radiating unit, and a decompression unit (16).
An evaporation unit (17) that evaporates the refrigerant and cools the heat medium by exchanging heat between the refrigerant decompressed by the decompression unit and the heat medium.
The outside air endothermic unit (45) that causes the heat medium cooled by the evaporation unit to absorb heat from the outside air,
A heat source (25, 82) that dissipates heat to the heat medium and heats the heat medium.
The first circulation circuit (20, 80) that circulates the heat medium to the heat source, and
A second circulation circuit (30) that circulates a heat medium between the evaporation section and the outside air heat absorption section,
It is determined whether or not the outside air heat absorbing portion needs to be defrosted, and the result is determined.
When it is determined that defrosting of the outside air heat absorbing portion is not necessary, the heat medium is circulated separately in the first circulation circuit and the second circulation circuit.
When it is determined that defrosting of the outside air heat absorbing portion is necessary, the flow path switching unit (26,) for switching the flow path of the heat medium so as to circulate the heat medium of the first circulation circuit to the outside air heat absorbing portion. 60, 83) and a refrigeration cycle device. The heat source dissipates the waste heat generated by the operation to the heat medium, and dissipates the waste heat to the heat medium.
The refrigeration cycle apparatus according to claim 1, wherein in the first circulation circuit, waste heat of the heat source is stored in the heat medium by circulating the heat medium in the heat source. An air heating unit (22) for heating the air by radiating the heat medium to the air blown into the vehicle interior is provided.
The heat radiating unit dissipates the refrigerant discharged from the compressor to the heat medium.
In the first circulation circuit, the heat medium is circulated in the heat radiating section, the heat source, and the air heating section.
When the flow path switching portion determines that defrosting of the outside air heat absorbing portion is necessary, the heat medium of the first circulation circuit is said to flow in parallel with the air heating portion and the outside air heat absorbing portion. The refrigerating cycle apparatus according to claim 1, wherein the flow path of the heat medium is switched. An air heating unit (22) for heating the air by radiating the heat medium to the air blown into the vehicle interior is provided.
The heat radiating unit dissipates the refrigerant discharged from the compressor to the heat medium.
The heat source includes a first heat source (82) that dissipates waste heat generated by operation to the heat medium, and a second heat source (25) that generates heat for heating the air.
The first circulation circuit includes a heat storage circuit (80) in which the waste heat of the first heat source is stored in the heat medium by circulating the heat medium in the first heat source, a heat dissipation unit, the second heat source, and the like. The air heating unit includes a heating circuit (20) for circulating the heat medium.
When the flow path switching section determines that defrosting of the outside air heat absorbing section is necessary, the flow path switching section switches the flow path of the heat medium so as to circulate the heat medium of the heat storage circuit to the outside air heat absorbing section. When it is determined that defrosting of the outside air heat absorbing portion is necessary after circulating the heat medium of the heat storage circuit to the outside air heat absorbing portion, the heat medium of the heating circuit is the heat radiating portion and the outside air heat absorbing portion. The refrigerating cycle apparatus according to claim 1, wherein the flow path of the heat medium is switched so as to flow in parallel with the heat medium. In the flow path switching portion, when the vehicle is traveling, the outside air heat absorbing portion is in a frosted state, and the temperature (TWW, TWH) of the heat medium of the first circulation circuit is a predetermined temperature (α1, The refrigerating cycle apparatus according to any one of claims 1 to 4, wherein it is determined that defrosting of the outside air heat absorbing portion is necessary when the temperature exceeds α2). In the flow path switching portion, when the occupant is performing air conditioning before boarding the vehicle, the outside air heat absorbing portion is in a frosted state, and the temperature of the heat medium of the first circulation circuit (TWW, TWH). The refrigerating cycle apparatus according to any one of claims 1 to 5, wherein when the temperature exceeds a predetermined temperature (α1, α2), it is determined that defrosting of the outside air heat absorbing portion is necessary. 2. 6. The refrigerating cycle apparatus according to any one of 6. Claim 1 determines that the flow path switching unit needs to defrost the outside air heat absorbing portion when the air conditioning before the occupant gets into the vehicle is completed and the outside air heat absorbing portion is in a frosted state. The refrigerating cycle apparatus according to any one of 7. The flow path switching portion determines whether or not the outside air heat absorbing portion is in a frosted state based on the temperature (TWR) of the heat medium flowing through the outside air heat absorbing portion and the temperature of the outside air (Tam). The refrigeration cycle apparatus according to any one of claims 5 to 8. The outside air heat absorbing section includes a first heat medium flow section (32) through which the heat medium cooled by the evaporation section flows, and a second heat medium flow section (23) through which the heat medium heated by the heat source flows. The refrigeration according to any one of claims 1 to 9, further comprising a heat transfer member (37) for heat-transferably connecting the first heat medium flow section and the second heat medium flow section. Cycle device.

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